JP3885904B2 - EGR gas cooling device - Google Patents

EGR gas cooling device Download PDF

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Publication number
JP3885904B2
JP3885904B2 JP13168397A JP13168397A JP3885904B2 JP 3885904 B2 JP3885904 B2 JP 3885904B2 JP 13168397 A JP13168397 A JP 13168397A JP 13168397 A JP13168397 A JP 13168397A JP 3885904 B2 JP3885904 B2 JP 3885904B2
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egr gas
cooling
cooling zone
temperature
tube
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JPH10306987A (en
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豊博 古屋
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Usui Co Ltd
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Usui Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、エンジンの冷却液、インタークーラー用冷媒、カーエアコン用冷媒または冷却風等によってＥＧＲガスを冷却する装置に関するものである。
【０００２】
【従来の技術】
排気ガスの一部を排気系から取出して、再びエンジンの吸気系に戻し、混合気に加える方法は、ＥＧＲ（Ｅｘｈａｕｓｔ Ｇａｓ Ｒｅｃｉｒｃｕｌａｔｉｏｎ：排気再循環）と称される。ＥＧＲはＮＯｘ（窒素酸化物）の発生抑制、ポンプ損失の低減、燃焼ガスの温度低下に伴う冷却液への放熱損失の低減、作動ガス量・組成の変化による比熱比の増大と、これに伴うサイクル効率の向上等、多くの効果が得られることから、エンジンの熱効率を改善するには有効な方法とされている。
【０００３】
しかるに、ＥＧＲガスの温度が高くなると、吸気温度の上昇に伴う燃費の低下やその熱作用によりＥＧＲバルブの耐久性が劣化し、早期破損を招く場合があったり、その防止のために水冷構造とする必要があること等が認識されている。このような事態を避けるため、エンジンの冷却液等によってＥＧＲガスを冷却する装置が用いられている。この装置としては、一般に多管式の熱交換器が利用される。
【０００４】
この場合に利用される多管式の熱交換器は、図２にその一例を示すごとく、両端部に冷却媒体流入口１１−１および冷却媒体流出口１１−２を設けた胴管１１内部において、伝熱管群１２の両端部がチューブシート１３にろう付けまたは溶接により固定され、一方チューブシート１３はその外周部を胴管１１の内壁にろう付けまたは溶接により固着して配列され、前記胴管１１の一方の端部にはＥＧＲガスの流入口１４ａ−１が設けられた端部キャップ１４ａが固着され、また他方の端部にはＥＧＲガスの流出口１４ｂ−１が設けられた端部キャップ１４ｂが固着された構成となし、冷却媒体流入口１１−１より導入されるエンジンの冷却液等により、伝熱管群１２の内部を流れるＥＧＲガスが冷却される構造となっているものが知られている（実公昭５７−３０９号公報等参照）。
【０００５】
【発明が解決しようとする課題】
しかしながら、エンジンの冷却液等によってＥＧＲガスを冷却する上記の多管式熱交換器の場合は、エンジンの冷却液がＥＧＲガスとの熱交換により昇温し、胴管１１内部において沸騰することや、エンジン冷却液の温度が１００℃に近くＥＧＲガスの出口付近では両流体間の温度差が少ないため伝熱管群１２の内部を流れるＥＧＲガスが十分に冷却されないという問題点があった。
【０００６】
本発明は、このような問題点を解決するためになされたもので、ＥＧＲガスの冷却ゾーンを複数で構成するとともに、各冷却ゾーンに温度の異なる冷却媒体を導入する方式をとることによって、冷却媒体の沸騰現象を防止するとともに、ＥＧＲガスの出口付近での温度差を大きくしてＥＧＲガスの熱交換量を高めることができるＥＧＲガス冷却装置を提供しようとするものである。
【０００７】
本発明は、上記課題を解決するため、胴管内壁の両端部付近に固定されたチューブシートに伝熱管群が固着配列され、さらに前記胴管の両端部の外側には端部キャップが固着され、また前記端部キャップにはＥＧＲガスの流入口と流出口が設けられた構造の多管式のＥＧＲガス冷却装置において、前記胴管の冷却ゾーンを仕切板にて両端と中央部の３つの冷却ゾーンに区分し、両端部の冷却ゾーンをそれぞれ第１冷却ゾーンおよび第３冷却ゾーン、中央部を第２冷却ゾーンとし、かつ前記第１冷却ゾーンと第３冷却ゾーン間を配管にて連通し、第１冷却ゾーンおよび第３冷却ゾーンには低温冷却媒体を、第２冷却ゾーンにはエンジン冷却液をそれぞれ導入する方式となしたことを特徴とするものである。
【０００８】
本発明において、主にＥＧＲガスの流入口側に設ける第１冷却ゾーンと、ＥＧＲガスの流出口側に設ける第３冷却ゾーンは、それぞれ胴管の全容積の５〜３０％程度が適当とされる。その理由は５％未満では胴管内部における沸騰の防止やＥＧＲガス出口付近での低温冷却媒体との温度差が乏しく、一方３０％を超えると低温冷却媒体の熱負荷が大きくなり過ぎるためであるが、低温冷却媒体の導入温度や伝熱管の径やピッチなどによっては必ずしもこの容積とする必要はない。また、胴管の両端部に低温冷却媒体を導入し、胴管中央部にエンジン冷却液を導入してＥＧＲガスを冷却するようにしたのは、なるべく多くの熱量をエンジン冷却液で冷却し低温冷却媒体の熱負荷を軽くすること、ＥＧＲガスを大温度差で能率よく冷却することと、エンジン冷却液の沸騰現象を防止するためである。低温冷却媒体としては、例えば水冷インタークーラー用冷却液やカーエアコン用冷媒等を使用することができる。
【０００９】
ＥＧＲガス流入口より流入したＥＧＲガスは、まず第１冷却ゾーンで低温冷却媒体により冷却される。このゾーンでは、ＥＧＲガスと低温冷却媒体との温度差が大きいので熱交換率が高い。したがって、ＥＧＲガスの温度が高くエンジン冷却液での冷却では伝熱管の外表面において当該冷却液の沸騰が発生するような場合、この第１冷却ゾーンでの冷却により沸騰を防止するかあるいは僅かに沸騰して小さな気泡が発生しても直ちに凝縮できる。次に、第１冷却ゾーンで冷却されたＥＧＲガスは中央の第２冷却ゾーンにおいて、エンジン冷却液により通常の冷却が行われ熱量の多くはこのゾーンで熱交換される。この第２冷却ゾーンでは、ＥＧＲガスとエンジン冷却液の温度差が小さくなるため、ＥＧＲガスの当該ゾーン出口温度はエンジン冷却液の温度にかなり近づく。第３冷却ゾーンでは、第１冷却ゾーンより配管を通って導入される低温冷却媒体により熱交換されるので、ＥＧＲガスと低温冷却媒体間の温度差が大きくなり（急冷効果）、ＥＧＲガスの温度を第２冷却ゾーンより下げることができる。
【００１０】
なお、胴管の両端と中央部の３つの冷却ゾーンは、一応仕切板によって水密に仕切られるが、両低温冷却媒体とエンジン冷却液が同系の場合は仕切板と伝熱管群とは完全密閉シールする必要はない。
【００１１】
【発明の実施の形態】
図１は本発明に係る多管式のＥＧＲガス冷却装置の構造例を示す横断平面図であり、１は胴管、１−１は第１冷却ゾーン、１−２は第２冷却ゾーン、１−３は第３冷却ゾーン、２は伝熱管群、３はチューブシート、４ａ、４ｂは端部キャップ、４ａ−１はＥＧＲガスの流入口、４ｂ−１はＥＧＲガスの流出口、５は仕切板、６は連絡配管である。
【００１２】
すなわち、本発明に係る多管式のＥＧＲガス冷却装置は、両端部に冷却媒体流入口１−１および冷却媒体流出口１−２を設けた胴管１内部において、伝熱管群２の両端部が板金製のチューブシート３にろう付けまたは溶接により固定され、一方チューブシート３はその外周部を胴管１の内壁にろう付けまたは溶接により固着して配列され、前記胴管１の一方の端部にはＥＧＲガスの流入口４ａ−１が設けられた端部キャップ４ａが固着され、また他方の端部にはＥＧＲガスの流出口４ｂ−１が設けられた端部キャップ４ｂが固着された構成となすとともに、胴管１内部の両端部に仕切板５をろう付けまたは溶接により固定し、胴管１内部のＥＧＲガスの流入口側を第１冷却ゾーン１−１、中央部を第２冷却ゾーン１−２、ＥＧＲガスの流出口側を第３冷却ゾーン１−３とし、かつ第１冷却ゾーン１−１と第３冷却ゾーン１−３を連絡配管６にて連通し、第１冷却ゾーン１−１には低温冷却媒体の流入口１−１ａを、第３冷却ゾーン１−３には低温冷却媒体の流出口１−３ｂを、第２冷却ゾーン１−２にはエンジン冷却液の流入口１−２ａと流出口１−２ｂを、それぞれ設けた構造となっている。
【００１３】
上記構造のＥＧＲガス冷却装置において、ＥＧＲガスの流入口４ａ−１より流入したＥＧＲガスは、第１冷却ゾーン１−１において低温冷却媒体流入口１−１ａより導入された低温冷却媒体により大温度差で能率よく冷却され、続いて第２冷却ゾーン１−２においてエンジン冷却液流入口１−２ａより導入されるエンジン冷却液にて通常の冷却が行われる。この第２冷却ゾーン１−２では、ＥＧＲガスとエンジン冷却液の温度差が小さくなるため、ＥＧＲガスの当該ゾーン出口温度はエンジン冷却液の温度にかなり近づいた状態で第３冷却ゾーン１−３に移行する。第３冷却ゾーン１−３では、第１冷却ゾーン１−１から連絡配管６を介して導入される低温冷却媒体により、エンジン冷却液の温度にかなり近づいたＥＧＲガスが大きな温度差（急冷効果）によりさらに冷却される。したがって、ＥＧＲガス流出口４ｂ−１より流出するＥＧＲガスは、エンジン冷却液のみにより冷却する従来のＥＧＲガス冷却装置よりも低温に冷却される。故に、ＮＯｘ（窒素酸化物）の発生を大幅に抑制できる上、パーティキュレートの減少および燃費の向上をはかることができる。なお、第１冷却ゾーン１−１の低温冷却媒体流入口１−１ａより導入された低温冷却媒体は、第３冷却ゾーン１−３に設けた低温冷却媒体流出口１−３ｂより流出し、第２冷却ゾーン１−１のエンジン冷却液流入口１−２ａより導入されたエンジン冷却液は当該ゾーンに設けたエンジン冷却液流出口１−２ｂより流出する。
【００１４】
なお図示の実施例では、ＥＧＲガスはまず第１冷却ゾーン１−１に導入され、次いで第２冷却ゾーン１−２を介して第３冷却ゾーン１−３から流出する例について説明したが、所望に応じＥＧＲガスの流れを逆にして、まず第３冷却ゾーン１−３に導入され、第２冷却ゾーン１−２を介して第１冷却ゾーン１−１から流出するよう構成しても上記と同様の作用効果が得られる。
【００１５】
【発明の効果】
以上説明したごとく、本発明のＥＧＲガス冷却装置によれば、ＥＧＲガスを３つの冷却ゾーンにて効率よく冷却することができることにより、ＥＧＲガスをエンジン冷却液のみにより冷却する従来のＥＧＲガス冷却装置よりも低温に冷却することができ、冷却媒体の沸騰現象を防止するとともに、ＥＧＲガスの出口付近での温度差を大きくしてＥＧＲガスの熱交換量を高めてＮＯｘ（窒素酸化物）の発生抑制、パーティキュレートの減少および燃費の向上に多大な効果を奏する。
【図面の簡単な説明】
【図１】本発明に係る多管式のＥＧＲガス冷却装置の構造例を示す横断平面図である。
【図２】本発明の対象とする従来の多管式のＥＧＲガス冷却装置の一例を一部破断して示す平面図である。
【符号の説明】
１ 胴管
１−１ａ 低温冷却媒体の流入口
１−２ａ エンジン冷却液の流入口
１−２ｂ エンジン冷却液の流出口
１−３ｂ 低温冷却媒体の流出口
２ 伝熱管群
３ チューブシート
４ａ、４ｂ 端部キャップ
４ａ−１ ＥＧＲガスの流入口
４ｂ−１ ＥＧＲガスの流出口
５ 仕切板
６ 連絡配管[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an apparatus that cools EGR gas with engine coolant, intercooler refrigerant, car air conditioner refrigerant, cooling air, or the like.
[0002]
[Prior art]
A method in which a part of the exhaust gas is taken out from the exhaust system, returned to the engine intake system, and added to the air-fuel mixture is called EGR (Exhaust Gas Recirculation). EGR suppresses the generation of NOx (nitrogen oxide), reduces pump loss, reduces heat dissipation loss to the coolant due to lowering of combustion gas temperature, and increases specific heat ratio due to changes in working gas amount / composition. Since many effects such as improvement of cycle efficiency can be obtained, it is an effective method for improving the thermal efficiency of the engine.
[0003]
However, when the temperature of the EGR gas increases, the durability of the EGR valve deteriorates due to a decrease in fuel consumption accompanying the increase in intake air temperature and its thermal action, which may lead to premature breakage. It is recognized that there is a need to do so. In order to avoid such a situation, an apparatus that cools EGR gas with engine coolant or the like is used. As this apparatus, a multi-tube heat exchanger is generally used.
[0004]
As shown in FIG. 2, the multi-tubular heat exchanger used in this case is provided inside the trunk tube 11 provided with the cooling medium inlet 11-1 and the cooling medium outlet 11-2 at both ends. Both ends of the heat transfer tube group 12 are fixed to the tube sheet 13 by brazing or welding, while the tube sheet 13 is arranged with its outer peripheral portion fixed to the inner wall of the trunk tube 11 by brazing or welding, An end cap 14a provided with an EGR gas inflow port 14a-1 is fixed to one end of the end 11, and an end cap provided with an EGR gas outflow port 14b-1 is provided at the other end. 14b is fixed, and the EGR gas flowing inside the heat transfer tube group 12 is cooled by engine coolant introduced from the coolant inlet 11-1 or the like. Have (See Publication No. Utility Model 57-309).
[0005]
[Problems to be solved by the invention]
However, in the case of the above-described multi-tube heat exchanger that cools the EGR gas with engine coolant or the like, the temperature of the engine coolant rises due to heat exchange with the EGR gas, and boiles in the trunk tube 11. The temperature of the engine coolant is close to 100 ° C., and the temperature difference between the two fluids is small near the outlet of the EGR gas, so that the EGR gas flowing inside the heat transfer tube group 12 is not sufficiently cooled.
[0006]
The present invention has been made in order to solve such problems, and includes a plurality of EGR gas cooling zones, and a cooling medium having different temperatures is introduced into each cooling zone. An object of the present invention is to provide an EGR gas cooling device that can prevent a medium boiling phenomenon and increase a temperature difference in the vicinity of the outlet of the EGR gas to increase the heat exchange amount of the EGR gas.
[0007]
In order to solve the above problems, the present invention has a heat transfer tube group fixedly arranged on a tube sheet fixed in the vicinity of both ends of the inner wall of the trunk tube, and end caps are fixed to the outside of both ends of the trunk tube. Further, in the multi-tube EGR gas cooling device having a structure in which an inlet and an outlet for EGR gas are provided in the end cap, the cooling zone of the trunk pipe is divided into three parts at both ends and a central part by a partition plate. It is divided into cooling zones, the cooling zones at both ends are the first cooling zone and the third cooling zone, the central portion is the second cooling zone, and the first cooling zone and the third cooling zone are connected by piping. The first cooling zone and the third cooling zone are configured to introduce a low-temperature cooling medium, and the second cooling zone is configured to introduce an engine coolant.
[0008]
In the present invention, the first cooling zone provided mainly on the EGR gas inlet side and the third cooling zone provided on the EGR gas outlet side are each appropriately set to about 5 to 30% of the total volume of the trunk pipe. The The reason is that if it is less than 5%, the temperature difference from the low temperature cooling medium in the vicinity of the EGR gas outlet and the prevention of boiling inside the trunk tube is poor, while if it exceeds 30%, the thermal load of the low temperature cooling medium becomes too large. However, this volume is not necessarily required depending on the introduction temperature of the low-temperature cooling medium, the diameter and pitch of the heat transfer tubes, and the like. In addition, the EGR gas is cooled by introducing a low-temperature cooling medium to both ends of the trunk and introducing an engine coolant to the middle of the trunk to cool the EGR gas as much as possible with the engine coolant. This is because the heat load of the cooling medium is reduced, the EGR gas is efficiently cooled with a large temperature difference, and the boiling phenomenon of the engine coolant is prevented. As the low-temperature cooling medium, for example, a coolant for a water-cooled intercooler, a refrigerant for a car air conditioner, or the like can be used.
[0009]
The EGR gas that has flowed in from the EGR gas inlet is first cooled by the low-temperature cooling medium in the first cooling zone. In this zone, since the temperature difference between the EGR gas and the low-temperature cooling medium is large, the heat exchange rate is high. Therefore, when the EGR gas temperature is high and the cooling of the engine coolant causes boiling of the coolant on the outer surface of the heat transfer tube, the cooling in the first cooling zone prevents the boiling or slightly Even if it boiles and small bubbles are generated, it can be condensed immediately. Next, the EGR gas cooled in the first cooling zone is normally cooled by the engine coolant in the central second cooling zone, and most of the heat is exchanged in this zone. In this second cooling zone, the temperature difference between the EGR gas and the engine coolant becomes small, so that the zone outlet temperature of the EGR gas approaches the temperature of the engine coolant considerably. In the third cooling zone, heat exchange is performed by the low-temperature cooling medium introduced through the pipe from the first cooling zone, so that the temperature difference between the EGR gas and the low-temperature cooling medium increases (rapid cooling effect), and the temperature of the EGR gas Can be lowered from the second cooling zone.
[0010]
Note that the three cooling zones at both ends and the center of the trunk are watertightly partitioned by a partition plate. However, if the low-temperature cooling medium and the engine coolant are the same system, the partition plate and the heat transfer tube group are completely sealed. do not have to.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 is a cross-sectional plan view showing a structural example of a multi-tube EGR gas cooling device according to the present invention, wherein 1 is a trunk pipe, 1-1 is a first cooling zone, 1-2 is a second cooling zone, -3 is a third cooling zone, 2 is a heat transfer tube group, 3 is a tube sheet, 4a and 4b are end caps, 4a-1 is an EGR gas inlet, 4b-1 is an EGR gas outlet, and 5 is a partition A plate 6 is a connecting pipe.
[0012]
That is, the multi-tube EGR gas cooling device according to the present invention includes both end portions of the heat transfer tube group 2 inside the trunk tube 1 provided with the cooling medium inlet port 1-1 and the cooling medium outlet port 1-2 at both ends. Is fixed to the tube sheet 3 made of sheet metal by brazing or welding, while the tube sheet 3 is arranged with its outer peripheral portion fixed to the inner wall of the barrel tube 1 by brazing or welding, and one end of the barrel tube 1 is arranged. An end cap 4a provided with an EGR gas inlet 4a-1 is fixed to the part, and an end cap 4b provided with an EGR gas outlet 4b-1 is fixed to the other end. In addition to the configuration, the partition plates 5 are fixed to both ends inside the trunk tube 1 by brazing or welding, the EGR gas inlet side inside the trunk tube 1 is the first cooling zone 1-1, and the central portion is the second. Cooling zone 1-2, EGR gas outlet Is the third cooling zone 1-3, and the first cooling zone 1-1 and the third cooling zone 1-3 are communicated with each other through the connecting pipe 6, and the inlet of the low-temperature cooling medium is connected to the first cooling zone 1-1. 1-1a, the third cooling zone 1-3 has a low-temperature cooling medium outlet 1-3b, the second cooling zone 1-2 has an engine coolant inlet 1-2a and an outlet 1-2b. Each has a structure provided.
[0013]
In the EGR gas cooling apparatus having the above-described structure, the EGR gas that has flowed in from the EGR gas inlet 4a-1 has a large temperature due to the low-temperature cooling medium introduced from the low-temperature cooling medium inlet 1-1a in the first cooling zone 1-1. Cooling is efficiently performed by the difference, and then normal cooling is performed with the engine coolant introduced from the engine coolant inlet 1-2a in the second cooling zone 1-2. In the second cooling zone 1-2, since the temperature difference between the EGR gas and the engine coolant is small, the zone cooling temperature of the EGR gas is considerably close to the temperature of the engine coolant. Migrate to In the third cooling zone 1-3, the EGR gas that has approached the temperature of the engine coolant is greatly affected by the low-temperature cooling medium introduced from the first cooling zone 1-1 via the connecting pipe 6 (rapid cooling effect). Is further cooled. Therefore, the EGR gas flowing out from the EGR gas outlet 4b-1 is cooled to a temperature lower than that of the conventional EGR gas cooling device that is cooled only by the engine coolant. Therefore, generation of NOx (nitrogen oxide) can be greatly suppressed, and particulates can be reduced and fuel consumption can be improved. The low-temperature cooling medium introduced from the low-temperature cooling medium inlet 1-1a in the first cooling zone 1-1 flows out from the low-temperature cooling medium outlet 1-3b provided in the third cooling zone 1-3. The engine coolant introduced from the engine coolant inlet 1-2a in the 2-cooling zone 1-1 flows out from the engine coolant outlet 1-2b provided in the zone.
[0014]
In the illustrated embodiment, EGR gas is first introduced into the first cooling zone 1-1 and then flows out from the third cooling zone 1-3 through the second cooling zone 1-2. Accordingly, the flow of the EGR gas is reversed, and the EGR gas is first introduced into the third cooling zone 1-3 and then flows out of the first cooling zone 1-1 through the second cooling zone 1-2. Similar effects can be obtained.
[0015]
【The invention's effect】
As described above, according to the EGR gas cooling device of the present invention, the EGR gas can be efficiently cooled in the three cooling zones, so that the conventional EGR gas cooling device that cools the EGR gas only by the engine coolant. It can be cooled to a lower temperature, preventing the boiling phenomenon of the cooling medium, and increasing the temperature difference near the outlet of the EGR gas to increase the heat exchange amount of the EGR gas and generate NOx (nitrogen oxide) It has a great effect on suppression, reduction of particulates and improvement of fuel consumption.
[Brief description of the drawings]
FIG. 1 is a cross-sectional plan view showing a structural example of a multi-tube EGR gas cooling device according to the present invention.
FIG. 2 is a plan view partially broken away showing an example of a conventional multi-tube EGR gas cooling device that is a subject of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Body pipe 1-1a Low temperature cooling medium inflow 1-2a Engine cooling liquid inflow 1-2b Engine cooling liquid outflow 1-3b Low temperature cooling medium outflow 2 Heat transfer tube group 3 Tube sheet 4a, 4b End Cap 4a-1 EGR gas inlet 4b-1 EGR gas outlet 5 Partition plate 6 Connecting piping

Claims (1)

胴管内壁の両端部付近に固定されたチューブシートに伝熱管群が固着配列され、さらに前記胴管の両端部の外側には端部キャップが固着され、また前記端部キャップにはＥＧＲガスの流入口と流出口が設けられた構造の多管式のＥＧＲガス冷却装置において、前記胴管の冷却ゾーンを仕切板にて両端と中央部の３つの冷却ゾーンに区分し、両端部の冷却ゾーンをそれぞれ第１冷却ゾーンおよび第３冷却ゾーン、中央部を第２冷却ゾーンとし、かつ前記第１冷却ゾーンと第３冷却ゾーン間を配管にて連通し、第１冷却ゾーンおよび第３冷却ゾーンには低温冷却媒体を、第２冷却ゾーンにはエンジン冷却液をそれぞれ導入する方式となしたことを特徴とするＥＧＲガス冷却装置。A heat transfer tube group is fixedly arranged on tube sheets fixed near both ends of the inner wall of the trunk tube, and end caps are fixed to the outside of both ends of the trunk tube, and EGR gas is attached to the end cap. In the multi-tube EGR gas cooling apparatus having a structure in which an inlet and an outlet are provided, the cooling zone of the trunk pipe is divided into three cooling zones at both ends and a central portion by a partition plate, and cooling zones at both ends Are the first cooling zone and the third cooling zone, the central portion is the second cooling zone, and the first cooling zone and the third cooling zone are connected by piping, and the first cooling zone and the third cooling zone are connected. Is a system for introducing a low-temperature cooling medium and an engine coolant into the second cooling zone, respectively.
JP13168397A 1997-05-06 1997-05-06 EGR gas cooling device Expired - Fee Related JP3885904B2 (en)

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JP13168397A JP3885904B2 (en) 1997-05-06 1997-05-06 EGR gas cooling device

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Publication number Priority date Publication date Assignee Title
JP2000045883A (en) * 1998-07-24 2000-02-15 Hino Motors Ltd Egr cooler
ITRM20010050A1 (en) * 2001-01-31 2002-07-31 Bennardo Marioli HIGH FLOW EXCHANGER MANIFOLD DEVICE.
DE10312788A1 (en) 2003-03-21 2004-09-30 Behr Gmbh & Co. Kg Exhaust gas heat exchanger and sealing device for exhaust gas heat exchanger
CN1300539C (en) * 2003-10-30 2007-02-14 丁振荣 Inner tube equipment of heating water by using disposal heat energy generated from condensation process
JP2007255719A (en) 2004-04-30 2007-10-04 T Rad Co Ltd Connection structure of heat exchanger
JP4578375B2 (en) * 2005-09-30 2010-11-10 日野自動車株式会社 Engine EGR system
DE102006055973A1 (en) * 2006-11-24 2008-05-29 Borsig Gmbh Heat exchanger for cooling cracked gas
US7461641B1 (en) 2007-10-18 2008-12-09 Ford Global Technologies, Llc EGR Cooling System with Multiple EGR Coolers
JP5293077B2 (en) * 2007-10-30 2013-09-18 株式会社デンソー Heat exchanger
KR101458352B1 (en) * 2008-07-21 2014-11-04 한라비스테온공조 주식회사 Radiator equipped with inverter cooling part
BE1019332A5 (en) 2010-05-11 2012-06-05 Atlas Copco Airpower Nv HEAT EXCHANGER.
JP5582022B2 (en) * 2010-12-22 2014-09-03 株式会社デンソー Exhaust heat exchanger
CN108775825B (en) * 2018-05-24 2021-05-04 重庆美的通用制冷设备有限公司 Heat exchange assembly and refrigerating system with same

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